SU1537930A1 - Toothed gearing - Google Patents

Abstract

The invention relates to mechanical engineering and can be used in power gears. The aim of the invention is to increase the service life. In a gear drive containing a drive and driven gears, the profiles of the heads of the teeth of which are outlined with convex curves, and the profiles of the legs of the teeth are outlined with concave curves, the profiles of the teeth are described by the following equations: X = ± XCOS (Α _W + ϕ) ± YSIN ( _W ± ϕ) ± R _W (SIN ϕ - ϕ ^. COS ϕ), Y = ± XSIN (Α _W ± ϕ) ± YCOS (Α _W ± ϕ) + R _W (COS ϕ + ϕ ^. SIN), where the upper signs of the arithmetic operations refer to the profile of the legs of the teeth, and the bottom - to the profile of the heads of the teeth

R _W - the radius of the initial circle of the gear

Α _W - the angle of engagement on the initial circle

φ = ^X. X @ + ^Y. Y @ / R _W (X @ ^. COSΑ _W + Y @ ^. SINΑ ^W ) - the angular coordinate of the gear

Y = ^M. Y @ ^. TGΑ / KX = M * 981 Y @ ^. TGΑDΑ Α = Α _I -Α _W , where M is the gear module, К = 0.001 ... 2.5, Α _I is the current value of the engagement angle. 3 il.

Description

x T Xcos (ot0 + tf) h - Ysin () T rw (sinq -C -coscp), y Xsin (ocw + tf) Ycos (ocw t /) 1- rw (cos q + cf.sine /),

where the upper signs of arithmetic actions refer to the profile of the legs of the teeth, and the lower signs to the profile of the heads of the teeth; rw is the radius of the initial circumference of the gear; Nc / engagement angle on the initial circle;

C X-X + Y-Y // I.

m / rw (X. costxLwt Y sinrt.uglo coordinate gear;

The invention relates to mechanical engineering and can be used in power gears.

The aim of the invention is to increase the service life by reducing the sensitivity of the transmission to changes in the center distance.

FIG. 1 shows a gear wheel tooth; in fig. 2 is a diagram for determining the coordinates of a production curve; in fig. 3 - spot form

x TXcos (oiw + H) 7 Ysin (wT y ± X sin () + Ycos (oCw +

Y tgoi / K; X ha J Y tg «ido;

about with /; -oi

w

with s

(L

where m is the gear module, К 0.001 ... 2.5, is the current value of the engagement angle. 4 il.

contact on the drive wheel; in fig. 4 - the same on the driven wheel tooth.

Gear gear, contains the leading and driven gears (not shown), the profiles of the heads of 1 teeth. which are outlined with convex curves, and the profiles of the legs of the 2 teeth are concave curves. The 3-tooth profiles are described by the equations C) rw (sin (j-Lp-costf);

C) + rw (cos (p + if sin (f),

ate

GO J

with

GO

The upper signs of arithmetic relate to the profile of the legs of the teeth, and the lower signs to the profile of the heads of the teeth;

X, Y - coordinates of tooth profiles;

rw is the radius of the initial circumference of the gear; Y fci vu angle of engagement on the initial circle;

h

Xx + y y1

r U cosc Y sino w) UGL °

va gear coordinate

Y - mY tg.t / K, X - m {-Y1,

de m - gear module; K 0.001 ... 2.5;

+ g di "j

Y ™ is a derivative of Y on wasps;

ubo (H v

X - - derivative from X to about,

QOO

cL d,

where ot; - the current value of the engagement angle.

In gearing, the radius of curvature of the profiles of the legs and the heads of the teeth of the wheels varies.

Assuming that the point with the angle ОС O of the profile of the generating curve always lies on the axis OX, since for O, Y and 0, to obtain the value of the angle of engagement on the initial circle, the initial PX prog is necessary –v Xcos (otw + q) 4- Ysin (udw4C |) G y Xcos (oiw + H) + Ycos (oiw) +

the lower signs of arithmetic relate to the profile of the legs of the teeth, and the lower signs to the profile of the heads of the teeth;

X, Y - coordinates of tooth profiles;

g is the radius of the initial circumference of the gear; 1 Angle of engagement on the initial circle;

„Х-Х + Y Y1

  r X cos f Y Sin T UGL °

five

five

turn the water curve by an angle w to the PX position (Fig. 2).

X, Y - coordinate axes rotated relative to the initial positions of the axes X, Y coordinates on an angle.

When the gearing operates in the zigzag phase of engagement due to the zigzag shape of the contact patch, a half-open cavity is created between the mating surfaces of the teeth. This cavity is open in the direction of movement of the contact spot, which ensures that it is filled with oil and creates pressure in it. This has a favorable effect on the creation of an oil film between the working surfaces of the mating teeth, reduces friction and increases the durability of the gear train. Since the cavity is open in the direction of movement of the contact spot in the polar phase of engagement, it is most efficient to use this transmission in the polar variant, when the drive wheel profiles of the teeth are outlined with convex portions of the curves, and the follower is concave.

Claims (1)

Invention Formula A gear drive containing a driving and driven gear, the tooth head profiles of which are outlined with convex curves, and the tooth foot profiles with concave curves, which, in order to increase the service life by reducing the transmission sensitivity to changing axle spacing, the tooth profiles are described by the following equations: rw (.sobf); r Ccostf + q. si nip), Y m 0 where is that TO five va coordinate gear wheels; Y1 tgei / K; X m J Y tgcAiiw, - gear module; 0.001 ... 2.5; dX   derived from X dY jЈ is a derivative of Y; about oL -oЈw,  where is the current value of the engagement angle. X Y Figg Fig.Z fig L